EP2689112B1 - Mechanically controllable valve drive and mechanically controllable valve drive arrangement - Google Patents
Mechanically controllable valve drive and mechanically controllable valve drive arrangement Download PDFInfo
- Publication number
- EP2689112B1 EP2689112B1 EP12701109.6A EP12701109A EP2689112B1 EP 2689112 B1 EP2689112 B1 EP 2689112B1 EP 12701109 A EP12701109 A EP 12701109A EP 2689112 B1 EP2689112 B1 EP 2689112B1
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- EP
- European Patent Office
- Prior art keywords
- valve drive
- wheel element
- controllable valve
- mechanically controllable
- drive according
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
- F01L13/0026—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio by means of an eccentric
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
Definitions
- the invention relates to a mechanically controllable valve drive with a gas exchange valve, which acts directly or indirectly on a transmission arrangement by means of a working contour, wherein the transmission assembly is movably mounted in the cylinder head by means of bearing and wherein the transmission assembly is in operative connection with a Ventilhubverstell responded and a camshaft, wherein the Ventilhubverstell responded a rotatable adjusting shaft, such that different maximum strokes are adjustable, wherein the transmission arrangement has a first and a second Radorgan, wherein the first Radorgan is in operative connection with the camshaft and the second Radorgan directly or indirectly the gas exchange valve acts, both Radorgane on the Adjusting shaft are rotatably mounted and have a toothing, such that the first and the second wheel member are so geared together, that an adjustment of the adjusting a phase nverschiebung between the first and the second Radorgan causes and that a rotational fixation causes an oscillating movement of the first and second Radorgans.
- a valve gear and a valve train arrangement are for example from the EP 638 706 A1 known.
- an eccentric shaft rotatably mounted in a cylinder head is provided for controlling or regulating the valve lift, which acts on the transmission arrangement such that in a simple way valve strokes between 0 and maximum can be set.
- valve trains / valve train arrangements have the disadvantage that an adjustment of the valve lift takes place via a translational and rotational movement of an intermediate lever of the transfer arrangement.
- a very complicated guide of the intermediate lever must be used, combined with tight manufacturing and assembly tolerances. Overall, this results in an expensive and difficult to control overall construction of the transmission arrangement.
- This valve train has the disadvantage that an adjustment requires a lot of effort. As a result, increased wear and a complex design of actuators is given.
- the object of the invention is therefore to provide a valve train or a valve train arrangement which avoids the above-mentioned disadvantages.
- the object is achieved in that the toothing is designed such that a rotation of the adjusting causes the phase shift.
- a mechanical valve train is created, which is designed so that only a rotational movement is required to ensure a valve lift.
- a much simpler storage of the transmission arrangement is possible and wear phenomena could be substantially minimized.
- a particularly advantageous embodiment is provided in that the first wheel member is biased by a spring element with respect to the camshaft. This also makes it possible that the adjusting shaft can be driven in both directions. Also games can be compensated in the gearing.
- a first, particularly advantageous embodiment of the invention is provided by the fact that the first and the second Radorgan are designed as mutually facing crown gears and the geared connection is made via at least one planetary gear, each planet gear is mounted on a rotatably connected to the adjusting shaft axis ,
- This embodiment is designed as a crown gear planetary gear.
- a second, particularly advantageous embodiment of the invention is characterized in that the first and the second wheel member are formed as internal gears, wherein the first wheel member has a different inner diameter with a different number of teeth than the second wheel member and that the adjusting shaft has an eccentric rotatable on the a first and a second spur gear are mounted, which are rotationally rigidly coupled to each other and which are respectively in engagement with the first and second Radorgan and thus establish the geared connection.
- the first and the second wheel member are formed as internal gears, wherein the first wheel member has a different inner diameter with a different number of teeth than the second wheel member and that the adjusting shaft has an eccentric rotatable on the a first and a second spur gear are mounted, which are rotationally rigidly coupled to each other and which are respectively in engagement with the first and second Radorgan and thus establish the geared connection.
- the first wheel member has a contact roller for the camshaft, so that the first wheel member is set by the continuously rotating camshaft in an oscillating rotation about the axis of the adjusting shaft.
- the second wheel member can be designed in an advantageous manner such that it has the working contour.
- the second Radorgan geared to a working contour having deflection member is connected, wherein the Auslenkorgan is rotatably and concentrically mounted on the camshaft. It is particularly advantageous assembly and production technology, when a drag lever is rotatably mounted on the adjusting shaft. In this way, a pre-testable, easy-to-install unit of transmission assembly and drag lever can be created.
- each cylinder is assigned a mechanically controllable valve drive according to one of claims 1 to 10, wherein each gas exchange valve is assigned in each case a working contour which acts directly or indirectly on the gas exchange valve.
- FIG. 1 1 shows an embodiment of a valve drive arrangement 10 according to the invention with a plurality of gas exchange valves 12, 14, 16, 18, 20 and 22 arranged in series.
- a drag lever 66 and the cross section of a valve rod of the respective gas exchange valves 12, 14, 16, 18, 20 and 22 which are arranged in known manner in cylinders 13, 15 and 17.
- two inlet gas exchange valves are assigned to a cylinder of the internal combustion engine.
- the mechanically controllable valve train arrangement 10 has three transmission arrangements 28, 30, 32 and 34, to which two gas exchange valves 12, 14; 16, 18; 20, 22 are assigned.
- the transmission arrangements 28, 30 and 32 are mounted on an adjusting shaft 35 in the cylinder head by means of bearing means 36.
- the bearing means 36 are in the present FIG. 1 merely exemplified for the storage of the adjusting shaft 35.
- each transmission arrangement comprises a first and a second wheel member 40, 42, wherein the first wheel member 40 is operatively connected via a contact roller 44 with a camshaft 46.
- Both Radorgane 40, 42 are rotatably mounted on the adjusting shaft 35 and are connected to each other geared such that a rotation of the adjusting 35 causes a phase shift between the first and second Radorgan 40, 42 and that a rotational fixation in the same direction oscillating movement of the first and second wheel member 40, 42 causes.
- the adjusting shaft 35 is drivable in the present embodiment by a drive member 48 in a known manner.
- a drive member 48 a rotary drive is used, which can run both forward and backward.
- the adjusting shaft 35 can thus be driven in such a way that, depending on the present position, the valve stroke corresponding to the next operating state is selected quickly and precisely. Even angles of rotation of> 360 ° can be realized.
- FIG. 2a shows a first embodiment of a mechanically controllable valve drive in longitudinal section.
- a valve drive is shown, which acts on a gas exchange valve 12.
- the adjusting shaft 35 is rotatably mounted in the cylinder head and can by the in FIG. 1 shown drive member 48 are rotated.
- the first wheel member 40 is rotatably mounted.
- the first wheel member 40 receives the freely rotatable contact roller 44 for the camshaft 46 via a fixed axle 50.
- the first wheel member 40 is formed as a crown wheel, whose teeth are directed to the second wheel member 42.
- the first wheel member 40 meshes with a plurality, preferably three planetary gears 54, two of which are shown in the present embodiment and which are each mounted on an axis 56 rotatably connected to the adjusting shaft.
- These Planet gears 54 mesh over their teeth 58 in turn with the teeth 60 of the likewise formed as a crown wheel second wheel member 42nd Wie der FIG. 2b can be seen, the second wheel member 42, the working contour 62, which is in operative connection with a roller 64 of the drag lever 66.
- the operation of the first embodiment is now as follows: With rotationally fixed adjusting shaft 35, the continuously rotating camshaft 46 via a cam 68, the first wheel member 40 in an oscillating about the adjusting shaft 35 movement. As a result, the planetary gears 54 also experience an oscillating movement, as a result of which a movement of the second wheel element 42 which oscillates in the opposite direction to the first wheel element 40 takes place. As a result, the gas exchange valve 12 is then opened on the working contour 62 and closed again in a known manner.
- FIG. 2b shows in cross section the first embodiment according to the invention, in which the gas exchange valve 12 is shown in the closed state.
- the first wheel member 40 Via a spring element 70, the first wheel member 40 is biased relative to the camshaft 46.
- the translation between the first wheel member 40 and the planetary gears 54 and between the planet gears 54 and the second wheel member 42 need not be identical be. A translation deviating from the 1: 1 ratio may be advantageous in certain applications.
- FIG. 3a shows a longitudinal section of a second embodiment of the invention.
- the first and the second wheel member 40, 42 are rotatably mounted on the adjusting shaft 35 again, wherein the first wheel member 40, as in the first embodiment, via the fixed axis 50 receives the freely rotatable contact roller 44 for the camshaft 46.
- the second wheel member 42 may, as in FIG. 2b illustrated, the working contour 62 have.
- the second wheel member 42 is formed so that the working contour 62 is positioned on an extension piece 72 of the wheel member 42.
- the eccentric 82 is formed in a known manner on the adjusting shaft 35.
- the first and second spur gears 78, 80 are integrally formed. In order to effect a phase shift between the first and second wheel members 40, 42, the first and second wheel members 40, 42 and the associated spur gears 78, 80 have a different number of teeth.
- the first wheel member 40 and the associated first spur gear 78 have a smaller diameter and thus a smaller number of teeth than the second Radorgan 42 and the associated second spur gear 80. This is a high reduction between the rotation of the adjusting 35 and the intended phase shift between realized the two Radorganen 40, 42.
- FIG. 3b shows in the present embodiment, the gas exchange valve 12 in the open state with the preset maximum valve lift.
- the operation of the second embodiment is now as follows: To represent a preset maximum stroke of the gas exchange valve 12 to be actuated, the adjusting shaft 35 is rotationally fixed.
- the continuously rotating camshaft 46 displaces the first wheel member 40 with its drive cam 68 in a movement oscillating about the adjusting shaft 35.
- About the geared connection of the first wheel member 40 with the second wheel member 42, and the second wheel member 42 undergoes a same direction oscillating motion.
- this oscillating motion is transmitted to the roller 64 of the drag lever 66 and thus the gas exchange valve 12 is opened in a known manner with the preset maximum stroke and closed again.
- FIG. 4a shows a longitudinal section of a third embodiment of the invention.
- This embodiment describes a particularly compact solution, since the entire transmission arrangement is to be stored only about two axes 35, 46.
- a particular advantage is that the position of the camshaft with respect to a valve train with a fixed maximum stroke does not have to be changed. Also, this unit can be easily and inexpensively mounted as a verifiable unit, since all components are stored in the two axes 35,46.
- first and a second wheel member 40, 42 are provided, which are rotatably mounted on the adjusting shaft 35.
- the first and second wheel member 40, 42 are designed as internal gears 74, 76 of different size and number of teeth, which are connected via two spur gears 78, 80 geared together.
- the spur gears 78, 80 are rotatably mounted as in the second embodiment on an eccentric 82 of the adjusting shaft 35 and corresponding to the meshing internal gears 74, 76 have a different size and number of teeth.
- the first wheel member 40 also has a fixed axle 50 (see FIG. 4b ), on which the contact roller 44 for the drive cam 68, which here has a different shape than in the preceding embodiments, is rotatably mounted.
- the second wheel member 42 also has an outer toothing 86, which is in operative connection with the external toothing 88 of a Auslenkorgans 90, which in turn is rotatably mounted on the camshaft 46 (see also Figure 4c ).
- the deflection element 90 has two deflection cams 92, which describe a working contour and which act on the roller 64 of a drag lever 66 of a gas exchange valve 12 in a known manner.
- the drag levers 66 are in turn rotatably mounted on the adjusting shaft 35 (see FIG. 4d ).
- a plate spring 84 which is supported on the bearing 36 of the camshaft 46 and on Auslenkorgan 90 in the axial direction, and the same direction, sliding profile displacements of the gear connection between external teeth 88 of the Auslenkorgans 90 and outer teeth 86 of the second Radorgans 42, between the second Radorgan 42 and the second spur gear 80, as well as between the first wheel member 40 and the first spur gear 78, the entire geared connection can be biased and the backlash be eliminated.
- the operation of the third embodiment is now as follows: With a preset maximum stroke of the gas exchange valve 12 to be actuated, the adjusting shaft 35 is rotationally fixed.
- the continuously rotating camshaft 46 displaces the first wheel member 40 with its drive cam 68 in a movement oscillating about the adjusting shaft 35.
- About the geared connection of the first wheel member 40 with the second wheel member 42 and the second wheel member 42 undergoes a like-minded oscillating movement.
- About the external gear teeth 86 of the second wheel member 42 then this oscillating movement is transmitted in an opposite, oscillating movement of the Auslenkorgans 90.
- Auslenknocken 92 which acts on the drag lever 66, the gas exchange valve 12 is then opened in a known manner with the preset maximum stroke and closed again.
- All described embodiments can be designed so that the deflection member performs an oscillating movement with only a small tilt angle. In this case, only a part of the entire circumference of the deflection element is used to vary the maximum valve lifts in the range between zero stroke and full stroke. It is therefore possible to apply a further and different working contour to the remaining part of the circumference. These contours can be e.g. be purposefully shut down individual gas exchange valves of a cylinder to ensure a more precise flow control and trigger a demand-based charge movement in the cylinder, or shut down all valves of a cylinder to represent a cylinder shutdown.
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Description
Die Erfindung betrifft einen mechanisch steuerbarer Ventiltrieb mit einem Gaswechselventil, auf das direkt oder indirekt eine Übertragungsanordnung mittels einer Arbeitskontur angreift, wobei die Übertragungsanordnung im Zylinderkopf mittels Lagermittel beweglich gelagert ist und wobei die Übertragungsanordnung mit einer Ventilhubverstelleinrichtung und einer Nockenwelle in Wirkverbindung steht, wobei die Ventilhubverstelleinrichtung eine drehbare Verstellwelle aufweist, derart, dass verschiedene Maximalhübe einstellbar sind, wobei die Übertragungsanordnung ein erstes und ein zweites Radorgan aufweist, wobei das erste Radorgan mit der Nockenwelle in Wirkverbindung steht und das zweite Radorgan direkt oder indirekt das Gaswechselventils einwirkt, wobei beide Radorgane auf der Verstellwelle drehbar gelagert sind und eine Verzahnung aufweisen, derart, dass das erste und das zweite Radorgan derart getrieblich miteinander verbunden sind, dass ein Verstellen der Verstellwelle eine Phasenverschiebung zwischen dem ersten und dem zweiten Radorgan bewirkt und dass eine rotatorische Fixierung eine oszillierende Bewegung des ersten und zweiten Radorgans bewirkt.The invention relates to a mechanically controllable valve drive with a gas exchange valve, which acts directly or indirectly on a transmission arrangement by means of a working contour, wherein the transmission assembly is movably mounted in the cylinder head by means of bearing and wherein the transmission assembly is in operative connection with a Ventilhubverstelleinrichtung and a camshaft, wherein the Ventilhubverstelleinrichtung a rotatable adjusting shaft, such that different maximum strokes are adjustable, wherein the transmission arrangement has a first and a second Radorgan, wherein the first Radorgan is in operative connection with the camshaft and the second Radorgan directly or indirectly the gas exchange valve acts, both Radorgane on the Adjusting shaft are rotatably mounted and have a toothing, such that the first and the second wheel member are so geared together, that an adjustment of the adjusting a phase nverschiebung between the first and the second Radorgan causes and that a rotational fixation causes an oscillating movement of the first and second Radorgans.
Ein Ventiltrieb sowie eine Ventiltriebanordnung sind beispielsweise aus der
Darüber hinaus ist es aus der
Aus der
Diese bekannten Ventiltriebe/Ventiltriebanordnungen weisen jedoch den Nachteil auf, dass eine Verstellung des Ventilhubes über eine translatorische und rotatorische Bewegung eines Zwischenhebels der Übertragungsanordnung stattfindet. Hierdurch muss auch eine sehr komplizierte Führung des Zwischenhebels eingesetzt werden, verbunden mit engen Fertigungs- und Montagetoleranzen. Insgesamt ergibt sich hierdurch eine teure und nur schwer kontrollierbare Gesamtkonstruktion der Übertragungsanordnung.However, these known valve trains / valve train arrangements have the disadvantage that an adjustment of the valve lift takes place via a translational and rotational movement of an intermediate lever of the transfer arrangement. As a result, a very complicated guide of the intermediate lever must be used, combined with tight manufacturing and assembly tolerances. Overall, this results in an expensive and difficult to control overall construction of the transmission arrangement.
Dieser Ventiltrieb weist den Nachteil auf, dass ein Verstellvorgang einen großen Kraftaufwand benötigt. Hierdurch ist ein erhöhter Verschleiß sowie eine aufwendige Auslegung von Aktuatoren gegeben.This valve train has the disadvantage that an adjustment requires a lot of effort. As a result, increased wear and a complex design of actuators is given.
Aufgabe der Erfindung ist es daher, einen Ventiltrieb bzw. eine Ventiltriebanordnung zu schaffen, der/die die o.g. Nachteile vermeidet.The object of the invention is therefore to provide a valve train or a valve train arrangement which avoids the above-mentioned disadvantages.
Die Aufgabe wird dadurch gelöst, dass die Verzahnung derart ausgeführt ist, dass ein Drehen der Verstellwelle die Phasenverschiebung bewirkt. Hierdurch wird ein mechanischer Ventiltrieb geschaffen, der so ausgelegt ist, dass lediglich eine rotatorische Bewegung benötigt wird, um eine Ventilhubverstellung zu gewährleisten. Hierdurch ist auch eine wesentlich einfachere Lagerung der Übertragungsanordnung möglich und Verschleißerscheinungen konnten wesentlich minimiert werden.The object is achieved in that the toothing is designed such that a rotation of the adjusting causes the phase shift. As a result, a mechanical valve train is created, which is designed so that only a rotational movement is required to ensure a valve lift. As a result, a much simpler storage of the transmission arrangement is possible and wear phenomena could be substantially minimized.
Eine besonders vorteilhafte Ausführungsform wird dadurch geschaffen, dass das erste Radorgan durch ein Federelement gegenüber der Nockenwelle vorgespannt ist. Hierdurch ist es auch möglich, dass die Verstellwelle in beide Richtungen angetrieben werden kann. Auch können Spiele in der Verzahnung ausgeglichen werden.A particularly advantageous embodiment is provided in that the first wheel member is biased by a spring element with respect to the camshaft. This also makes it possible that the adjusting shaft can be driven in both directions. Also games can be compensated in the gearing.
Eine erste, besonders vorteilhafte erfindungsgemäße Ausführungsform wird dadurch bereit gestellt, dass das erste und das zweite Radorgan als zueinander gerichtete Kronenräder ausgebildet sind und das die getriebliche Verbindung über mindestens ein Planetenrad hergestellt ist, wobei jedes Planetenrad auf einer drehfest mit der Verstellwelle verbundenen Achse gelagert ist. Diese Ausführung ist ein als Kronenradgetriebe ausgebildetes Planetenradgetriebe.A first, particularly advantageous embodiment of the invention is provided by the fact that the first and the second Radorgan are designed as mutually facing crown gears and the geared connection is made via at least one planetary gear, each planet gear is mounted on a rotatably connected to the adjusting shaft axis , This embodiment is designed as a crown gear planetary gear.
Eine zweite, besonders vorteilhafte erfindungsgemäße Ausführungsform zeichnet sich dadurch aus, dass das erste und das zweite Radorgan als Innenzahnräder ausgebildet sind, wobei das erste Radorgan einen anderen Innendurchmesser mit anderer Zähnezahl als das zweite Radorgan aufweist und dass die Verstellwelle einen Exzenter aufweist, auf dem drehbar ein erstes und ein zweites Stirnzahnrad gelagert sind, die drehstarr miteinander gekoppelt sind und die jeweils in Eingriff mit dem ersten und zweiten Radorgan stehen und somit die getriebliche Verbindung herstellen. Mit einer derartigen Ausführungsform kann auf einfache Art und Weise im Falle einer Ausführung mit geringerer Zähnezahldifferenz zwischen erstem und zweitem Radorgan eine hohe Untersetzung der Verstellwelle gegenüber der Phasenverschiebung zwischen dem ersten und dem zweiten Radorgan hergestellt werden. Durch diese hohe, interne Untersetzung sind zum Einen nur geringe Aktuatorkräfte zum Antrieb der Verstellwelle erforderlich und zum Anderen ist eine sehr genaue Einstellung der maximalen Ventilhübe der Gaswechselventile möglich. Hierbei ist es montage- und fertigungstechnisch besonders vorteilhaft, wenn das erste und das zweite Stirnzahnrad einteilig ausgeführt sind. Ein besonders kompakt ausgeführter mechanisch steuerbarer Ventiltrieb wird dadurch geschaffen, dass das zweite Radorgan drehbar auf der Umfangsfläche des ersten Radorgans gelagert ist.A second, particularly advantageous embodiment of the invention is characterized in that the first and the second wheel member are formed as internal gears, wherein the first wheel member has a different inner diameter with a different number of teeth than the second wheel member and that the adjusting shaft has an eccentric rotatable on the a first and a second spur gear are mounted, which are rotationally rigidly coupled to each other and which are respectively in engagement with the first and second Radorgan and thus establish the geared connection. With such an embodiment can easily in the case of a design with less Number of teeth difference between the first and second Radorgan a high reduction of the adjusting against the phase shift between the first and the second Radorgan be prepared. By this high, internal reduction only a small Aktuatorkräfte for driving the adjusting shaft are required and on the other hand, a very accurate adjustment of the maximum valve lift the gas exchange valves possible. In this case, it is particularly advantageous in terms of assembly and production if the first and the second spur gears are made in one piece. A particularly compact designed mechanically controllable valve drive is created in that the second wheel member is rotatably mounted on the peripheral surface of the first wheel member.
Auch ist es vorteilhaft, wenn das erste Radorgan eine Kontaktrolle für die Nockenwelle aufweist, so dass das erste Radorgan durch die kontinuierlich rotierende Nockenwelle in eine oszillierende Rotation um die Achse der Verstellwelle versetzt wird. Das zweite Radorgan kann in vorteilhafter Weise derart ausgeführt sein, dass es die Arbeitskontur aufweist.It is also advantageous if the first wheel member has a contact roller for the camshaft, so that the first wheel member is set by the continuously rotating camshaft in an oscillating rotation about the axis of the adjusting shaft. The second wheel member can be designed in an advantageous manner such that it has the working contour.
Bei einer dritten, besonders vorteilhaften erfindungsgemäßen Ausführungsform der Erfindung das zweite Radorgan getrieblich mit einem die Arbeitskontur aufweisenden Auslenkorgan verbunden ist, wobei das Auslenkorgan drehbar und konzentrisch auf der Nockenwelle gelagert ist. Dabei ist es montage- und fertigungstechnisch besonders vorteilhaft, wenn ein Schlepphebel auf der Verstellwelle drehbar gelagert ist. Auf diese Art und Weise kann ein vorprüfbare, leicht zu montierende Einheit aus Übertragungsanordnung und Schlepphebel geschaffen werden.In a third, particularly advantageous embodiment of the invention, the second Radorgan geared to a working contour having deflection member is connected, wherein the Auslenkorgan is rotatably and concentrically mounted on the camshaft. It is particularly advantageous assembly and production technology, when a drag lever is rotatably mounted on the adjusting shaft. In this way, a pre-testable, easy-to-install unit of transmission assembly and drag lever can be created.
Die Aufgabe wird ebenfalls durch eine mechanisch steuerbare Ventiltriebanordnung gelöst, bei der jedem Zylinder ein mechanisch steuerbarer Ventiltrieb nach einem der Ansprüche 1 - 10 zugeordnet ist, wobei jedem Gaswechselventil jeweils eine Arbeitskontur zugeordnet ist, die direkt oder indirekt auf das Gaswechselventil einwirkt.The object is likewise achieved by a mechanically controllable valve drive arrangement in which each cylinder is assigned a mechanically controllable valve drive according to one of claims 1 to 10, wherein each gas exchange valve is assigned in each case a working contour which acts directly or indirectly on the gas exchange valve.
Die Erfindung wird nachfolgend anhand der Zeichnung näher erläutert, hierin zeigen:
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Figur 1 eine Darstellung im Schnitt einer erfinderischen Ventiltriebanordnung, -
Figur 2a und3b eine erste Ausführungsform eines erfindungsgemäßen Ventiltriebs im Längs- und Querschnitt, -
Figur 3a und 3b eine zweite Ausführungsform eines erfindungsgemäßen Ventiltriebs im Längs- und Querschnitt, und -
Figur 4a, 4b, 4c und 4d eine dritte Ausführungsform eines erfindungsgemäßen Ventiltriebs in einem Längsschnitt und drei Querschnitten.
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FIG. 1 a representation in section of an inventive valve train assembly, -
FIG. 2a and3b a first embodiment of a valve gear according to the invention in longitudinal and cross-section, -
Figure 3a and 3b a second embodiment of a valve gear according to the invention in the longitudinal and cross-section, and -
FIGS. 4a, 4b, 4c and 4d a third embodiment of a valve gear according to the invention in a longitudinal section and three cross sections.
Wie später noch ausführlicher beschrieben wird, weist jede Übertagungsanordnung ein erstes und ein zweites Radorgan 40, 42 auf, wobei das erste Radorgan 40 über eine Kontaktrolle 44 mit einer Nockenwelle 46 in Wirkverbindung steht. Beide Radorgane 40, 42 sind auf der Verstellwelle 35 drehbar gelagert und sind derart getrieblich miteinander verbunden, dass ein Drehen der Verstellwelle 35 eine Phasenverschiebung zwischen dem ersten und dem zweiten Radorgan 40, 42 bewirkt und dass eine rotatorische Fixierung eine gleichsinnige oszillierende Bewegung des ersten und zweiten Radorgans 40, 42 bewirkt.As will be described in more detail later, each transmission arrangement comprises a first and a
Die Verstellwelle 35 ist im vorliegenden Ausführungsbeispiel durch ein Antriebsorgan 48 auf bekannte Weise antreibbar. Als Antriebsorgan 48 wird ein Drehantrieb benutzt, der sowohl vorwärts wie auch rückwärts laufenden kann. Die Verstellwelle 35 kann damit derart angetrieben werden, dass in Abhängigkeit von der vorliegenden Position schnell und präzise der dem nächsten Betriebszustand entsprechende Ventilhub gewählt wird. Auch Drehwinkel von > 360° sind damit realisierbar.The adjusting
Die Funktionsweise des ersten Ausführungsbeispiels ist nun wie folgt: Bei rotatorisch fixierter Verstellwelle 35 versetzt die kontinuierlich drehende Nockenwelle 46 über einen Nocken 68 das erste Radorgan 40 in eine um die Verstellwelle 35 oszillierende Bewegung. Hierdurch erfahren auch die Planetenräder 54 eine oszillierende Bewegung, wodurch schließlich eine zum ersten Radorgan 40 gegensinnig oszillierende Bewegung des zweiten Radorgans 42 erfolgt. Hierdurch wird dann auf bekannte Weise das Gaswechselventil 12 über die Arbeitskontur 62 geöffnet und wieder geschlossen.The operation of the first embodiment is now as follows: With rotationally fixed adjusting
Soll nun der Maximalhub des Gaswechselventils 12 geändert werden, erfolgt durch das Antriebsorgan 48 ein Verdrehen der Verstellwelle 35. Durch dieses Verdrehen werden die festen Achsen 56 der Planetenräder 54 in Drehrichtung der Verstellwelle 35 bewegt, wodurch die Phasenbeziehung zwischen dem ersten und dem zweiten Radorgan 40, 42 geändert wird und dementsprechend die Rolle 64 des Schlepphebels 66 während der Öffnungs- und Schließbewegung mit einem anderen Abschnitt der Arbeitskontur 62 in Kontakt tritt.If now the maximum stroke of the
Die getriebliche Verbindung zwischen dem ersten und dem zweiten Radorgan 40, 42, die in diesem Fall als Innenzahnräder 74, 76 ausgeführt sind, wird bei diesem zweiten Ausführungsbeispiel durch ein erstes und ein zweites Stirnzahnrad 78, 80 hergestellt, die drehbar auf einem Exzenter 82 angeordnet sind. Der Exzenter 82 ist auf bekannte Weise an der Verstellwelle 35 ausgebildet. Vorteilhafterweise sind das erste und das zweite Stirnzahnrad 78, 80 einstückig ausgebildet. Um eine Phasenverschiebung zwischen dem ersten und zweiten Radorgan 40, 42 zu bewirken, weisen das erste und das zweite Radorgan 40, 42 sowie die dazugehörigen Stirnzahnräder 78, 80 eine unterschiedliche Zähnezahl auf. Im vorliegenden Ausführungsbeispiel haben das erste Radorgan 40 und das zugehörige erste Stirnzahnrad 78 einen geringeren Durchmesser und damit eine geringere Zähnezahl als das zweite Radorgan 42 und das zugehörige zweite Stirnzahnrad 80. Hierdurch wird eine hohe Untersetzung zwischen der Rotation der Verstellwelle 35 und der beabsichtigten Phasenverschiebung zwischen den beiden Radorganen 40, 42 realisiert. Über eine Tellerfeder 84, die sich am Lager 36 der Verstellwelle 35 abstützt, und einer gleichsinnigen, gleitenden Profilverschiebung der Zahnradverbindung zwischen dem ersten Radorgan 40 und dem ersten Stirnzahnrad 78 einerseits, sowie zwischen dem zweiten Radorgan 42 und dem zweiten Stirnzahnrad 80 andererseits kann die gesamte getriebliche Verbindung vorgespannt werden und Zahnflankenspiel eliminiert werden.The geared connection between the first and
Die Funktionsweise des zweiten Ausführungsbeispiels ist nun wie folgt: Zur Darstellung eines voreingestellten Maximalhubs des zu betätigenden Gaswechselventils 12 ist die Verstellwelle 35 rotatorisch fixiert. Die kontinuierlich drehende Nockenwelle 46 versetzt das erste Radorgan 40 mit seinem Antriebsnocken 68 in eine um die Verstellwelle 35 oszillierende Bewegung. Über die getriebliche Verbindung des ersten Radorgans 40 mit dem zweiten Radorgan 42, erfährt auch das zweite Radorgan 42 eine gleichsinnige oszillierende Bewegung. Über die Arbeitskontur 62 des Ansatzstückes 72 des zweiten Radorgans 42 wird dann diese oszillierende Bewegung auf die Rolle 64 des Schlepphebels 66 übertragen und damit das Gaswechselventil 12 auf bekannte Weise mit dem voreingestellten Maximalhub geöffnet und wieder geschlossen.The operation of the second embodiment is now as follows: To represent a preset maximum stroke of the
Soll nun der Maximalhub des Gaswechselventils 12 geändert werden, erfolgt auch hier durch das Antriebsorgan 48 ein Verdrehen der Verstellwelle 35. Durch dieses Verdrehen wird auch die Position des Exzenters 82 verändert und das erste und zweite Stirnzahnrad 78, 80 gleichsinnig gedreht. Aufgrund der unterschiedlichen Größen und Zähnezahlen der Zahnradpaarungen "erstes Radorgan - erstes Stirnzahnrad" 40, 78 und "zweites - Radorgan - zweites Stirnzahnrad" 42, 80, findet jedoch eine Phasenverschiebung zwischen dem ersten Radorgan 40 und dem zweiten Radorgan 42 statt. Dementsprechend wird auch das Ansatzstück 72 des zweiten Radorgans 42 um einen gewünschten Winkel verdreht, so dass die Rolle 64 des Schlepphebels 66 während der Öffnungs- und Schließbewegung mit einem anderen Abschnitt der Arbeitskontur 62 des Ansatzstückes des zweiten Radorgans 42 in Kontakt tritt.If now the maximum stroke of the
Wie beim Ausführungsbeispiel gemäß den
Das erste Radorgan 40 besitzt ebenfalls eine feststehende Achse 50 (siehe
Das zweite Radorgan 42 weist noch eine Aussenverzahnung 86 auf, die in Wirkverbindung mit der Aussenverzahnung 88 eines Auslenkorgans 90 steht, das wiederum drehbar auf der Nockenwelle 46 gelagert ist (siehe auch
Über eine Tellerfeder 84, die sich am Lager 36 der Nockenwelle 46 sowie am Auslenkorgan 90 in axialer Richtung abstützt, sowie gleichsinnigen, gleitenden Profilverschiebungen der Zahnradverbindung zwischen Aussenverzahnung 88 des Auslenkorgans 90 und Aussenverzahnung 86 des zweiten Radorgans 42, zwischen dem zweiten Radorgan 42 und dem zweiten Stirnzahnrad 80, sowie zwischen dem ersten Radorgan 40 und dem ersten Stirnzahnrad 78 kann die gesamte getriebliche Verbindung vorgespannt werden und das Zahnflankenspiel eliminiert werden.Via a
Die Funktionsweise des dritten Ausführungsbeispiels ist nun wie folgt: Bei einem voreingestellten Maximalhub des zu betätigenden Gaswechselventils 12 ist die Verstellwelle 35 rotatorisch fixiert. Die kontinuierlich drehende Nockenwelle 46 versetzt das erste Radorgan 40 mit seinem Antriebsnocken 68 in eine um die Verstellwelle 35 oszillierende Bewegung. Über die getriebliche Verbindung des ersten Radorgans 40 mit dem zweiten Radorgan 42 erfährt auch das zweite Radorgan 42 eine gleichgesinnte oszillierende Bewegung. Über die Aussenradverzahnung 86 des zweiten Radorgans 42 wird dann diese oszillierende Bewegung in eine gegensinnige, oszillierende Bewegung des Auslenkorgans 90 übertragen. Durch den Auslenknocken 92, der auf den Schlepphebel 66 angreift, wird dann das Gaswechselventil 12 auf bekannte Weise mit dem voreingestellten Maximalhub geöffnet und wieder geschlossen.The operation of the third embodiment is now as follows: With a preset maximum stroke of the
Soll nun der Maximalhub des Gaswechselventils 12 geändert werden, erfolgt auch hier durch das Antriebsorgan 48 ein Verdrehen der Verstellwelle 35. Durch dieses Verdrehen, wird auch die Position des Exzenters 82 verändert und damit auch das erste und zweite Stirnzahnrad 78, 80 gleichsinnig gedreht. Aufgrund der unterschiedlichen Größen und Zähnezahlen der Zahnradpaarungen "erstes Radorgan - erstes Stirnzahnrad" 40, 78 und "zweites - Radorgan - zweites Stirnzahnrad" 42, 80, findet eine Phasenverschiebung zwischen dem ersten Radorgan 40 und dem zweiten Radorgan 42 statt. Dementsprechend wird auch das Auslenkorgan 90, um einen gewünschten Winkel verdreht, so dass die Rolle 64 des Schlepphebels 66 während der Öffnungs- und Schließbewegung mit einem anderen Abschnitt des Auslenknockens 92 in Kontakt tritt.If now the maximum stroke of the
Besondere Vorteile entstehen bei dieser Ausführungsform gemäß
Alle beschriebenen Ausführungsformen können so gestaltet werden, dass das Auslenkorgan eine oszillierende Bewegung mit nur geringem Schwenkwinkel ausführt. Dabei wird zur Variation der maximalen Ventilhübe im Bereich zwischen Nullhub und Vollhub nur ein Teil des gesamten Umfangs des Auslenkorgans genutzt. Es ist also möglich, auf den restlichen Teil des Umfangs eine weitere und andere Arbeitskontur aufzubringen. Diese Konturen können z.B. dazu genutzt werden, einzelne Gaswechselventile eines Zylinders gezielt stillzulegen, um eine präzisere Mengensteuerung zu gewährleisten und eine bedarfsgerechte Ladungsbewegung im Zylinder auszulösen, oder auch alle Ventile eines Zylinders stillzulegen, um eine Zylinderabschaltung darzustellen.All described embodiments can be designed so that the deflection member performs an oscillating movement with only a small tilt angle. In this case, only a part of the entire circumference of the deflection element is used to vary the maximum valve lifts in the range between zero stroke and full stroke. It is therefore possible to apply a further and different working contour to the remaining part of the circumference. These contours can be e.g. be purposefully shut down individual gas exchange valves of a cylinder to ensure a more precise flow control and trigger a demand-based charge movement in the cylinder, or shut down all valves of a cylinder to represent a cylinder shutdown.
Claims (11)
- A mechanically controllable valve drive having a gas exchange valve (12) on which a transmission arrangement acts directly or indirectly by means of a working contour (62; 92), wherein the transmission arrangement is mounted in a movable manner in the cylinder head by bearing means, and wherein the transmission arrangement is operatively connected to a valve stroke adjusting device and to a camshaft (46), wherein the valve stroke adjusting device has a rotatable adjusting shaft (35) such that different maximum strokes can be set, the transmission arrangement having a first and a second wheel element (40, 42), wherein the first wheel element (40) is operatively connected to the camshaft (46) and the second wheel element (42) acts directly or indirectly on the gas exchange valve (12), wherein the two wheel elements (40, 42) are rotatably mounted on the adjusting shaft (35) and have a toothing, in such a way that the first and the second wheel element (40, 42) are in geared connection with one another such that a rotation of the adjusting shaft (35) effects a phase shift between the first and the second wheel element (40, 42) and such that rotary fixing is effective to generate an oscillating movement of the first and second wheel elements (40, 42), characterized in that the toothing is realized such that rotation of the adjusting shaft (35) causes the phase shift.
- The mechanically controllable valve drive according to claim 1, characterized in that the first wheel element (40) is biased relative to the camshaft (46) by a spring element (70).
- The mechanically controllable valve drive according to claim 1 or 2, characterized in that the first and the second wheel element (40, 42) are formed as mutually confronting crown gears and that the gear connection is realized via at least one planetary gear (54), each planetary gear (54) being supported on an axis connected to the adjusting shaft (35) for common rotation therewith.
- The mechanically controllable valve drive according to claim 1, characterized in that the first and the second wheel element (40, 42) are formed as internal gears, wherein the first wheel element (40) has a different inner diameter with a different number of teeth than the second wheel element (42), and that the adjustment shaft (35) comprises an eccentric (82) having a first and a second spur gear (78, 80) rotatably supported thereon which are coupled to each other in a torsionally rigid manner and are in engagement with the first and respectively the second wheel element (40, 42) and thus form the gear connection.
- The mechanically controllable valve drive according to claim 4, characterized in that the first and the second spur gears (78, 80) are formed as one part.
- The mechanically controllable valve drive according to claim 4 or 5, characterized in that the second wheel element (42) is rotatably supported on the peripheral surface of the first wheel element (40).
- The mechanically controllable valve drive according to any one of the preceding claims, characterized in that the first wheel element (40) comprises a contact roll (44) for the camshaft (46).
- The mechanically controllable valve drive according to any one of the preceding claims, characterized in that the second wheel element (42) comprises a working contour (62).
- The mechanically controllable valve drive according to any one of claims 4 to 7, characterized in that the second wheel element is in geared connection with a deflecting member (90) comprising said working contour (62), said deflecting member (90) being rotatably and concentrically supported on the camshaft (46).
- The mechanically controllable valve drive according to claim 9, characterized in that a drag lever (66) is rotatably supported on the adjusting shaft (35).
- A mechanically controllable valve drive arrangement comprising a plurality of serially arranged gas exchange valves assigned to a plurality of cylinders, characterized in that each cylinder has assigned thereto a mechanically controllable valve drive according to any one of claims 1 to 10, wherein each gas exchange valve has assigned thereto a respective working contour which directly or indirectly acts on the gas exchange valve.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201110014744 DE102011014744B4 (en) | 2011-03-22 | 2011-03-22 | Mechanically controllable valve drive and mechanically controllable valve train arrangement |
PCT/EP2012/051020 WO2012126648A1 (en) | 2011-03-22 | 2012-01-24 | Mechanically controllable valve drive and mechanically controllable valve drive arrangement |
Publications (2)
Publication Number | Publication Date |
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EP2689112A1 EP2689112A1 (en) | 2014-01-29 |
EP2689112B1 true EP2689112B1 (en) | 2014-12-10 |
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Application Number | Title | Priority Date | Filing Date |
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EP12701109.6A Not-in-force EP2689112B1 (en) | 2011-03-22 | 2012-01-24 | Mechanically controllable valve drive and mechanically controllable valve drive arrangement |
Country Status (8)
Country | Link |
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US (1) | US9133737B2 (en) |
EP (1) | EP2689112B1 (en) |
JP (1) | JP2014508892A (en) |
KR (1) | KR101541634B1 (en) |
CN (1) | CN103429859A (en) |
DE (1) | DE102011014744B4 (en) |
ES (1) | ES2530805T3 (en) |
WO (1) | WO2012126648A1 (en) |
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DE102016004531A1 (en) * | 2016-04-13 | 2017-10-19 | Man Truck & Bus Ag | Variable valve train with a rocker arm |
Family Cites Families (20)
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EP0638706A1 (en) | 1993-08-05 | 1995-02-15 | Bayerische Motoren Werke Aktiengesellschaft | Valve actuating mechanism of an internal combustion engine |
US6016779A (en) | 1996-09-02 | 2000-01-25 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating system in internal combustion engine |
JPH10331616A (en) | 1997-05-29 | 1998-12-15 | Honda Motor Co Ltd | Valve gear of internal combustion engine |
MY120554A (en) | 1997-10-29 | 2005-11-30 | Honda Motor Co Ltd | Valve operating system in internal combustion engine |
DE10235677B4 (en) | 2002-08-03 | 2005-03-03 | Gkn Driveline International Gmbh | One-sided axial securing of gears in crown gear drives |
US6951522B2 (en) | 2003-01-23 | 2005-10-04 | Torque-Traction Technologies, Inc. | Active differential assembly |
DE10312961C5 (en) * | 2003-03-24 | 2009-01-29 | Thyssenkrupp Presta Teccenter Ag | Device for the variable actuation of gas exchange valves of internal combustion engines |
JP4075811B2 (en) * | 2004-01-14 | 2008-04-16 | トヨタ自動車株式会社 | Variable valve mechanism failure diagnosis device for internal combustion engine |
JP2006017031A (en) | 2004-07-01 | 2006-01-19 | Denso Corp | Actuator for valve lift control device |
DE102005040959A1 (en) | 2005-08-30 | 2007-03-08 | Bayerische Motoren Werke Ag | Hubvariabler valve drive for an internal combustion engine |
JP2007127189A (en) | 2005-11-02 | 2007-05-24 | Toyota Motor Corp | Rotation-linear motion actuator, direct-acting shaft mechanism, variable valve train and variable valve system engine |
JP4265608B2 (en) * | 2006-01-17 | 2009-05-20 | トヨタ自動車株式会社 | Control device for variable valve mechanism |
US7475661B2 (en) * | 2006-10-17 | 2009-01-13 | Delphi Technologies, Inc. | Camshaft phaser having a differential bevel gear system |
JP2009062895A (en) | 2007-09-06 | 2009-03-26 | Denso Corp | Valve timing adjusting device |
JP2010048097A (en) | 2008-08-19 | 2010-03-04 | Toyota Motor Corp | Variable valve train for internal combustion engine |
DE102009007454A1 (en) * | 2009-02-04 | 2010-08-19 | Josef Astner | Angular gearing unit, especially crown-wheel gearing unit, has a crown-wheel device, a toothed-wheel device and a gearing element |
JP5294156B2 (en) | 2009-11-12 | 2013-09-18 | スズキ株式会社 | Variable valve operating device for internal combustion engine |
JP2011127489A (en) * | 2009-12-17 | 2011-06-30 | Suzuki Motor Corp | Variable valve gear of internal combustion engine |
JP2011231742A (en) * | 2010-04-30 | 2011-11-17 | Suzuki Motor Corp | Variable valve gear for internal combustion engine |
JP5625616B2 (en) * | 2010-08-20 | 2014-11-19 | スズキ株式会社 | Variable valve operating device for internal combustion engine |
-
2011
- 2011-03-22 DE DE201110014744 patent/DE102011014744B4/en not_active Expired - Fee Related
-
2012
- 2012-01-24 WO PCT/EP2012/051020 patent/WO2012126648A1/en active Application Filing
- 2012-01-24 EP EP12701109.6A patent/EP2689112B1/en not_active Not-in-force
- 2012-01-24 CN CN2012800140538A patent/CN103429859A/en active Pending
- 2012-01-24 ES ES12701109T patent/ES2530805T3/en active Active
- 2012-01-24 JP JP2014500296A patent/JP2014508892A/en active Pending
- 2012-01-24 KR KR1020137024851A patent/KR101541634B1/en not_active IP Right Cessation
- 2012-01-24 US US14/006,322 patent/US9133737B2/en not_active Expired - Fee Related
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KR20140004764A (en) | 2014-01-13 |
JP2014508892A (en) | 2014-04-10 |
US9133737B2 (en) | 2015-09-15 |
KR101541634B1 (en) | 2015-08-06 |
CN103429859A (en) | 2013-12-04 |
ES2530805T3 (en) | 2015-03-06 |
WO2012126648A1 (en) | 2012-09-27 |
EP2689112A1 (en) | 2014-01-29 |
DE102011014744A1 (en) | 2012-09-27 |
DE102011014744B4 (en) | 2015-04-30 |
US20140000538A1 (en) | 2014-01-02 |
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